Rotary seal arrangement

ABSTRACT

A rotary seal arrangement has a rotatably mounted machine part and a machine part that forms a bearing for the rotatably mounted machine part. One of the machine parts forms a seal accommodating structure and the other one of the machine parts has a surface forming a sealing surface. At least one rotary seal is arranged in the seal accommodating structure. The rotary seal seals off a high-pressure area from a low-pressure area between the machine parts.

The invention relates to a rotary seal arrangement, comprising arotatably mounted machine part, a machine part that forms a bearing forthe rotatably mounted machine part, wherein a first of the machine partsforms a seal-accommodating structure and the second of the machine partshas a surface forming a sealing surface, and at least one rotary sealarranged in the seal-accommodating structure. The rotary seal allows toseal off a high-pressure area from a low-pressure area between themachine parts.

Rotary seals of this kind are used, for example, to seal rotaryfeed-throughs. The high-pressure area is then constituted by a rotaryfeed-through area between the two machine parts. The rotary seal is alsotermed a rotary feed-through seal. The rotary feed-through permitsfluids, that is, gases or liquids, a sealed transition between astationary machine part and a rotating machine part. The first machinepart having the seal-accommodating structure is usually constituted asthe stationary machine part and the second machine part, as a shaftmounted rotatably within it. Such rotary feed-throughs are used, forexample, in hydraulic applications or to input hot gas for heating aroller.

Known rotary feed-throughs seals are constituted, for example, as asliding ring (mechanical seal) wherein the sliding ring usually has asealing ring made of polytetrafluoroethylene (PTFE).

An example of such a rotary feed-through seal is described in DE 10 2007062 470 A1. A rotary feed-through seal is designed such that as littlefluid as possible, which is under positive pressure, enters thelow-pressure area from the rotary feed-through area, that is, it issubject to low leakage. However, the lower the leakage, the greater thefriction occurring between the sealing surface of the rotatably mountedmachine part and the rotary feed-through seal. The wear of the rotaryfeed-through seal is correspondingly higher and a relatively largeamount of driving energy is expended against that friction force. Inparticular, when shafts rotate at high speeds and with fluids under highpressure, the life of such known rotary feed-through seals is thereforeshort.

Moreover, entrained rotation of the rotary seal with the shaft must beavoided. This is frequently achieved by pressing the sealing ring into aholding element that is also ring-shaped and is made, for example, ofsteel. The holding element is mounted torsionally rigidly in theseal-accommodating structure. However, such a rotary feed-through sealis relatively complicated to manufacture. For torsionally rigidmounting, an anti-rotation element must be provided on theseal-accommodating structure and/or the holding element must be pressedinto the seal-accommodating structure. Mounting in a simple slot,functioning as the seal-accommodating structure, is not possible becauseof the rigidity of the holding element.

The object of the invention is to provide a rotary seal arrangement thatavoids the disadvantages of the prior art, wherein, in particular,simple mounting of the rotary seal between the machine parts is possibleand entrained rotation of the sealing ring of the rotary seal isreliably avoided.

This task is solved by the elements of the independent claims. Thedependent claims disclose preferred embodiments of the invention.

An inventive rotary seal arrangement has a rotatably mounted machinepart and a machine part that forms a bearing for the rotatably mountedmachine part, wherein a first of the machine parts constitutes aseal-accommodating structure and the second of the machine parts has asurface forming a sealing surface. At least one rotary seal disposed inthe seal-accommodating structure is provided to seal a high-pressurearea against a low-pressure area between the machine parts. Thehigh-pressure area is at least temporarily under positive pressurerelative to the pressure of the low-pressure area.

According to the invention, the rotary seal has an essentially rigidsupport element that is disposed essentially positionally stably withrespect to the first machine part, a rubber-elastically deformablecontact body in contact with the support element on the high-pressurearea side, and a sealing ring that has a sealing edge and is in loosecontact with the contact body.

The sealing ring has a wide side on both sides of the sealing edge and aseal seat edge area facing away from the sealing edge. The wide sidesare interconnected via the seal seat edge area and the contact body isdisposed at least partially between one of the wide sides of the sealingring and the support element.

If the sealing surface is constituted as the lateral surface of acylinder, that is, as the lateral surface of a rotating shaft, thecontact body is disposed in the axial direction, that is, the directionof the axis of rotation, of the machine part mounted rotatably betweenthe support element and the sealing ring.

If the sealing surface is constituted as a circle area or a circularring area, that is, as an end face surface of a rotating shaft, thecontact body is disposed in the radial direction, that is, perpendicularto the direction of the axis of rotation, of the machine part mountedrotatably between the support element and the sealing ring.

The contact body does not have to be disposed completely between thesupport element and the sealing ring. It can also extend beyond thisarea. “In loose contact” means that the sealing ring is not constitutedintegrally with the contact body. The sealing ring can be pressedagainst the contact body by the design of the rotary seal so that itsrelative position with respect to the contact body is fixed by frictionforces occurring between the sealing ring and the contact body. Thesealing ring does not have to be permanently in contact with the contactbody. It can be in contact with the contact body only during a period inwhich a high pressure above a limit value determined by the design ofthe rotary seal is present in the high-pressure area, that is, it ispressed onto the contact body by the high pressure.

Due to the at least temporary pressing of the sealing ring against therubber-elastic contact body, the relative position of the sealing ringwith respect to the contact body is fixed by the friction forcesoccurring between the sealing ring and the contact body. The contactbody is pressed evenly against the support element and/or can beconstituted integrally with the support element. This reliably avoidsentrained rotation of the sealing ring with the rotatably mountedmachine part.

Simple mounting of the rotary seal is possible, in particular, if thesupport element is constituted integrally with the first machine part aspart of the seal-accommodating structure. The seal-accommodatingstructure can be constituted as a ring-shaped slot. Because noadditional rigid support element has to be provided, the sealing ringand, if not integrally constituted with the support element, the contactbody can simply be inserted or clamped in the seal-accommodatingstructure as elastically deformable parts.

The inventive rotary seal arrangement is suitable, in particular, forrotary feed-throughs in which the second machine part is constituted asa radial shaft mounted in the first machine part, wherein the rotaryseal is constituted in the shape of a ring and is disposed around theradial shaft. The rotary feed-through is therefore part of a pressuresupply of a pressure accumulator whose pressure can be regulated and/orset as required.

If the contact body extends in the radial direction of the rotary sealbetween the sealing ring and the seal-accommodating structure, thesealing ring can be pretensioned in the radial direction toward thesecond machine part due to an elastic return force of the contact body.In this way, the force with which the sealing edge is pressed onto thesealing surface can be predetermined by the design of the rotary seal.

The contact body preferably has an area that is in contact with thesealing ring in the axial direction of the rotatably mounted machinepart on the high-pressure area side. In this way, the edge of thesealing ring facing radially away from the sealing surface, that is, theseal seat edge area is disposed in a recess of the contact body. Thisedge then forms a type of pivot around which the sealing ring can tiltto a greater or lesser degree with alternating relative pressuredifferences between the high-pressure area and the low-pressure area sothat the force with which the sealing edge is pressed onto the sealingsurface can be dynamically adapted.

The inventive seal arrangement is especially preferably constituted as arotary feed-through. In this case, the high-pressure area is constitutedby a rotary feed-through area wherein, through the rotary feed-througharea, a fluid that is under a positive pressure relative to thelow-pressure area can be introduced from one of the machine partsthrough the sealing surface into the other of the machine parts. Thatis, the two machine parts together form a rotary feed-through and therotary seal is disposed between the machine parts as a rotaryfeed-through seal. The rotary feed-through area forms the high-pressurearea that is at least temporarily under positive pressure relative tothe pressure of the low-pressure area.

The support element especially preferably extends, at least in asupporting area, obliquely with respect to the axial direction of therotatably mounted machine part such that the sealing ring is pressedaway from the sealing surface in the supporting area by the contactbody. That is, the contact body is constituted such that the sealingring with the sealing edge is pressed against internal elastic forces ofthe contact body toward the sealing edge when the contact body ispressed together from its sealing ring side by an applied positivepressure relative to the low-pressure area. This especially effectivelyreduces the frictional forces acting on the rotary feed-through sealbetween the sealing surface of the rotatably mounted machine part andthe rotary feed-through seal.

In this way, it can be achieved that in a state without positivepressure, or a state with a pressure below a threshold value, in therotary feed-through area, the sealing edge is essentially in contactwith the sealing surface without a pressing force or is at a distancefrom the sealing surface. In a state with positive pressure, or a statewith a pressure above the threshold value, in the rotary feed-througharea, on the other hand, the sealing edge is in contact with the sealingsurface in such a way as to provide a seal because the fluid underpressure then exerts a force component on the sealing ring actingagainst pressing away by the contact body. Therefore, an increasedsealing effect is only achieved by the contacting sealing lip if arelatively high pressure is applied in the rotary feed-through area,that is, if the fluid in the rotary feed-through area is under arelatively high pressure. Because in very many applications of rotaryfeed-throughs, the fluid is only temporarily under high pressure, or anespecially high pressure is only temporarily applied to it, low frictionof the rotary seal with low leakage is achieved in this way. Forexample, if the fluid is a hot gas used to heat a roller, the sealingedge can then only be pressed forcefully onto the sealing surface if thehot gas is pressed into the roller with high pressure, for example, toheat the roller temporarily. Only in such a heating area is rotation ofthe roller significantly slowed by the sealing edge pressed against thesealing surface. If no hot gas is currently being pressed in, forexample, because the operating temperature of the roller has beenreached, the pressure of the fluid in the rotary feed-through area willdrop and the sealing edge will, for example, be lifted from the sealingsurface because the sealing ring is pressed away from the sealingsurface by the contact body which is, in particular, elasticallypretensioned and/or pressed away.

If the sealing ring has a cross-section that is angled concavely withrespect to the rotary feed-through area, a force pressing the sealingedge onto the sealing surface against the internal elastic forces of thecontact body can be generated especially well by the positive pressureprevailing at least temporarily in the sealing feed-through area of thefluid. The rotary feed-through area of the sealing ring and the sealingsurface are delimited in such a way that there is an obtuse anglebetween the rotary feed-through area side surface of the sealing ringand the sealing surface.

The support element can be made of a rigid plastic or a metal,preferably of steel. The sealing ring can advantageously be made ofPTFE, that is, polytetrafluorethylene PUR (polyurethane). Low-wear,rubber-elastic materials such as FKM (fluorinated elastomer), or HNBR(rubber-elastic materials) can also be used as materials for the sealingring. The contact body is preferably made of elastomer. It is importantthat it exhibits a rubber-elastic spring behavior.

If two rotary seals are preferably disposed mirror-symmetrically aroundthe, or a, rotary feed-through area, the rotary feed-through area isreliably sealed off on both sides.

The invention is explained in more detail below based on examples withreference to the drawings. The drawings each show a cross-sectionoriented axially with respect to the rotatably mounted machine part,wherein only an upper half of the seal arrangement is shown in eachcase.

The FIGS. 1 a and 1 b show a preferred embodiment of an inventive rotaryseal arrangement for sealing off a sealing surface constituted as thelateral surface of a cylinder.

FIG. 2 shows a further embodiment of an inventive rotary sealarrangement on a rotary feed-through.

FIG. 3 shows a further embodiment of an inventive rotary sealarrangement.

FIG. 4 shows an embodiment of an inventive rotary seal arrangement forsealing off a rotary feed-through in an end face of a rotatably mountedmachine part.

FIGS. 5 a to 5 e show embodiments of rotary seals of an inventive rotaryseal arrangement.

FIG. 6 shows an embodiment of a contact body of an inventive rotary sealarrangement.

FIG. 7 shows a further embodiment of an inventive rotary seal, similarto the rotary seal in FIG. 3.

FIGS. 8 a to 8 h show further embodiments of rotary seals of aninventive rotary seal arrangement.

The representations in the drawings show the inventive object in a veryschematic way and are not to scale. The individual parts of theinventive object are shown in such a way that their structure can beclearly illustrated.

FIGS. 1 a and 1 b show cross-sections of a preferred embodiment of aninventive rotary seal arrangement 1. Rotary seals 5 are mounted betweena rotatably mounted machine part 2 (shaft) and a machine part 3 thatforms a bearing for the rotatably mounted machine part 2. The rotaryseals therefore have a ring shape that is symmetrical about the centerof the ring. The rotatability of the shaft is symbolically shown in thefigure by a curved double arrow. The second machine part 2 isconstituted as a radial shaft mounted in the first machine part 3,wherein the rotary seals 5 are constituted in a ring shape and aredisposed around the radial shaft. The axis of rotational symmetry 6 ofthe rotary seals 5 coincides with the axis of rotation of the radialshaft.

Alternatively, the machine part 3 can rotate around the machine part 2.

The rotary seals 5 are inserted in a seal-accommodating structureconstituted by the first of the machine parts 3. The seal-accommodatingstructure does not have to be constituted by special shaping of theinternal surface of the first, that is, the stationary machine part 3,as shown in the figure. The seal-accommodating structure may only be anarea of surface that is not further specified, on which a rotary seal ispositioned. The second of the machine parts 2, that is, the radial shaftin the case shown, has a surface forming a sealing surface 7 that isformed as the lateral surface of a cylinder. The seat of the rotaryseals 5 is secured by a disk 8, which is in turn fixed by means of aspring washer 9 engaging in a slot.

By means of the rotary seals 5, a high-pressure area 10 constituted as arotary feed-through area is sealed off from a low-pressure area 11between the machine parts 2, 3. Through the rotary feed-through area 10,a fluid that is under positive pressure relative to the low-pressurearea 11 with the low pressure PN can be introduced from the stationarymachine part 3 through the sealing surface 7 into the rotatable machinepart 3. The low pressure PN can, for example, be standard atmosphericpressure. For this purpose, a hole 14 is provided in the stationarymachine part 3 that opens into the rotary feed-through area 10. Therotatable machine part 2 also has holes 14 that exit into the rotaryfeed-through area 10 and connect the rotary feed-through area 10 to oneshaft end of the rotatable machine part 2 for leading through the fluid.The fluid can therefore be introduced through the holes 14 from thestationary machine part 3 into the rotatable machine part 2, which issymbolically shown by arrows 16 in the figure. The fluid can also flowagainst the direction of the arrows 16 if required.

Two rotary seals 5 are disposed mirror-symmetrically around thehigh-pressure area 10, or the rotary feed-through area. Each of therotary seals 5 has an essentially rigid support element 20 that isdisposed essentially positionally stably with respect to the firstmachine part 3, a rubber-elastically deformable contact body 21 incontact with the support element 20 on the rotary feed-through areaside, and a sealing ring 23 that has a sealing edge 22 and a sealingring 23 in loose contact with contact body 21.

Each of the sealing rings 23 has a wide side 24 on both sides of itssealing edge 22 and a seal seat edge area 26 facing away from thesealing edge. The wide sides 24 of each sealing ring 23 areinterconnected via the corresponding seal seat edge area 26 and eachcontact body 21 is disposed between one of the wide sides 24 of eachsealing ring 23 and the associated support element 20. The wide sides 24form surface areas that constitute, at least on one of the sides of thesealing edge 22, a sufficient engagement surface for the fluid that isunder pressure in the high-pressure area to press the sealing ring 23onto the sealing surface 7 with the sealing edge 22 so as to provide aseal. The sealing ring 23 can, in particular, have the shape of a flatcircular ring, preferably deformed concavely within itself, wherein theedge pointing radially inward constitutes the sealing edge 7.

The sealing rings 23 are therefore not permanently connected to theassociated contact body 21 but are only in contact with it. There mayalso be interstices. The support element 20 is a component that isseparate from the machine parts 2,3. The sealing edge 22 of the sealingrings 23 is disposed in each case on a load area of each sealing ring 23protruding toward the sealing surface 7 beyond the support element 20and the interposed contact body 21. In particular, this load area isvariable in its position in the high-pressure area 10 when pressure isapplied. When pressure is applied, the load area is therefore deformedin such a way that the sealing edge 22 is pressed onto the sealingsurface 7.

The sealing rings 23 are each pressed away from the sealing surface 7 bythe associated contact body 21. This is shown symbolically by arrows 25in the figure. Pressing away is effected by the rubber-elasticproperties of the contact body 21. The sealing rings 23 each have across-section that is angled concavely with respect to the rotaryfeed-through area 10. The rotary feed-through area 10 is delimited bythe sealing rings 23 and the sealing surface 7 in such a way that thereis an obtuse angle between the rotary feed-through area side surfaces ofthe sealing rings 23 and the sealing surface 7. The contact bodies 21rest against each associated support element 20.

If a fluid under high pressure PH is introduced into the rotaryfeed-through area 10, as shown by the curved arrows in the figure, aforce is exerted on the rotary feed-through area side surfaces of thesealing rings 23. This force presses the contact bodies 21 togetheragainst their internal rubber-elastic return forces which press thesealing ring 23 away from the sealing surface 7. This presses thesealing edges 22 onto the sealing surface 7 in such a way that therotary feed-through area 10 is sealed essentially without leakageagainst the low-pressure area 11.

In the seal arrangement shown in FIG. 1 a, the two rotary seals 5 havean identical radial diameter. Accordingly, the seal-accommodatingstructure, into which the rotary seals 5 are mounted, also have the sameinside diameter on both sides of the hole 14 in the stationary machinepart 3.

In FIG. 1 b, the two rotary seals 5 each have a different radialdiameter. Accordingly, the seal-accommodating structure into which therotary seals 5 are mounted also have a different inside diameter on bothsides of the hole 14 in the stationary machine part 3, forming a step 29of the inside diameter.

FIG. 2 shows a further embodiment of an inventive rotary sealarrangement on a rotary feed-through. The rotary seal arrangement isessentially the same as the embodiment shown in FIG. 1 a, which is whythe relevant features are referred to with the same reference symbols.Unlike the embodiment in FIG. 1 a, the contact bodies 21 of the rotaryseals 5 shown in FIG. 2 each have a bulge 30 in their area adjacent tothe hole 14 in the stationary machine part 3. The bulges of the contactbodies 21 touch in such a way that they function as a non-return valve.If a fluid under high pressure is introduced through the hole 14 in thestationary machine part 3 in the direction of the arrow 16, the bulgesare pressed apart so that the fluid is introduced into the high-pressurearea 10. If the pressure of the fluid is reduced, the bulges 30 reclosethe hole 14 in the stationary machine part 3 due to the elastic returnforces of the rubber-elastic material of the contact bodies 21.

FIG. 3 shows a further embodiment of an inventive rotary sealarrangement. As in FIG. 1, the rotary seal 5 of the rotary sealarrangement is disposed for sealing off a high-pressure area 10,constituted as a rotary feed-through area, from a low-pressure area 11on a rotary feed-through between a second machine part 2, constituted asa rotatable shaft, and a first machine part 3, constituted as itsbearing. In the figure, the rotary seal arrangement parts correspondingto FIG. 1 are referred to using the same reference symbols.

Unlike the embodiment in FIG. 1, the support element 20 is constitutedintegrally with the second machine part 2. The support element 20 isconstituted by the low-pressure-side edge of a slot constituting theseal-accommodating structure into which the rubber-elastic contact body21 and the sealing ring 23 are inserted.

The sealing ring 23 is clamped in the slot by the contact body 21. Thecontact body 21 has an area in contact with the sealing ring 23 on thehigh-pressure side in the axial direction of the rotatably mountedmachine part 2. The edge of the sealing ring 23 facing radially awayfrom the sealing surface is thus disposed in a recess of the contactbody 21. At least when a sufficient positive pressure is applied in thehigh-pressure area 10, the sealing ring 23 is pressed firmly on the areaof the contact body 21 disposed between the supporting 20 and thesealing ring 23 so that entrained rotation of the sealing ring 23 withthe shaft is prevented. The pressing of the sealing ring 23 onto thecontact body is shown symbolically in the figure by an arrow in the areaof the sealing surface.

The contact body 21 also extends in the radial direction of the rotaryseal 5 between the sealing ring 23 and the seal-accommodating structure.The sealing ring 23 is pretensioned in the radial direction toward thesecond machine part 2 due to an elastic return force of the contact body21. This causes the contact body 21, which is M-shaped in its basicshape, to be pressed with its upper two ends 60 that are pointed whenuncompressed into the slot base of the slot. For that reason, the twoends 60 are shown rounded in the figure. The flexible mounting of thesealing ring 23 in the slot provided in this way is made yet moreflexible by cavities between the slot base and the contact body 21and/or between the contact body 21 and the sealing ring. Because thesealing ring 23 can easily tip over when pressure is applied, thesealing edge 22 can be flattened, or the sealing edge 22 forms two edgesthat seal alternatively against the sealing surface 7, depending on thepressure applied.

FIG. 4 shows an embodiment of an inventive rotary seal arrangement withtwo rotary seals 5 for sealing off a rotary feed-through in an end faceof a rotatably mounted machine part 2. End face refers to a side of therotatable machine part 2 to the surface of which the axis of rotation ofthe rotatable machine part 2, i.e. its axial direction, isperpendicular. Characteristics that are the same as the rotary sealarrangement of FIG. 1 a are referred to by the same reference symbols.The end face of the rotating machine part 2 forms the sealing surface 7and is constituted as a circular ring area. The contact bodies 21 aredisposed in the radial direction of the rotatably mounted machine part 2between the corresponding support element 20 and each sealing ring 23.The stationary machine part 3 has, on both sides of a hole 14 for afluid supply, a ring-shaped slot as a seal-accommodating structure intowhich the rotary seals 5 are inserted. On each of the slot edges of theslots facing away from the hole, a notch 32 is provided into which, ineach case, a projection 33 provided on the support elements 20 engages,whereby the rotary seals 5 are fixed in their position axially withrespect to the rotary machine part 2.

FIGS. 5 a to 5 e show axial cross-sections of different embodiments ofrotary seals of an inventive rotary seal arrangement. The embodimentsare essentially the same as the rotary seal according to FIG. 1. Forthis reason, only special details will be described here. In thefigures, the rotary seal arrangement parts corresponding to those inFIG. 1 are referred to by the same reference symbols. The contact bodies21 of the rotary seals shown each have a foot-like widened section onthe seal-accommodating structure side. The contact body extends in theradial direction of the rotary seal 5 between the sealing ring 23 andthe seal-accommodating structure, and the contact body 21 has an area incontact with the sealing ring 23 in the axial direction of the rotatablymounted machine part 2 on the high-pressure area side. The latter areaextends different distances toward the sealing edge. The edge of thesealing ring 23 facing radially away from the sealing surface is thusdisposed in a recess of the contact body 21.

The contact bodies 21 each have at least one end 60 coming to a point onthe sealing accommodating side. These ends 60 are pressed onto theseal-accommodating structure in such a way that the contact body 21 iselastically deformed, providing pretensioning of the sealing ring 23.This is symbolized by the dashed-line representation of the ends 60. Inthis way, the edge of the sealing ring 23 facing radially away from thesealing surface is also elastically clamped in the recess in the contactbody 21 in each case. In FIG. 5 b, this is effected by an edge 70bridging a space. The rotary seals differ further in the shaping of thesupport elements 20, the sealing rings 23, and the areas of the contactbodies 21 between them.

In FIGS. 5 a to 5 e, the support elements 20, the sealing rings 23 andthe areas of the contact bodies 21 between them each have across-section that is angled concavely with respect to the high-pressurearea. In this case, in the embodiments of FIGS. 5 c to 5 e, the area ofthe contact body 21 disposed between the support element 20 and thesealing ring 23 becomes conically wider toward the sealing edge. In FIG.5 f, on the other hand, the cross-section of the support element 20, ofthe sealing ring 23, and of the area of the contact body 21 between themare not angled.

All the embodiments shown have the common feature that, in each case,the sealing ring 23 is pretensioned in the radial direction toward thesecond machine part 2, which is not shown, due to an elastic returnforce of the contact body 21. Because the support element 20 extendsobliquely with respect to the axial direction of the rotatably mountedmachine part (not shown) at least in a respective supporting area, thecontact body 21 is pressed together in this area between the supportelement 20 and the sealing ring due to this pretensioning. This in turnpresses the sealing ring 23 in the supporting area away from the sealingsurface due to the contact body 21. The contact body 21 is disposed ineach respective supporting area radially between each support element 20and the associated sealing ring 23.

FIG. 6 shows an embodiment of the contact body 21 of an inventive rotaryseal arrangement in an axially oriented plan view. It therefore showsthe surface of the contact body 21 on the sealing ring side. The contactbody can also have flat surfaces on the sealing ring side; in thisembodiment, however, the surface has projections 80 toward the sealingring so that a distance between the contact body 21 and the sealing ringis retained when the contact body 21 is compressed.

FIG. 7 shows an axial cross-section of a further embodiment of aninventive rotary seal similar to the rotary seal in FIG. 3. The twopointed ends 60 of the contact body 21 provided for compression and adistance 85 on both sides between the contact body 21 and the sealingring 23 can be seen. The distances 85 can be filled after insertion ofthe contact body 21 and of the sealing ring into a slot of aseal-accommodating structure due to axial compression of the contactbody 21, whereby the sealing ring 23 of the contact body 21 can besecurely clamped.

FIGS. 8 a to 8 h show axial cross-sections of various embodiments ofrotary seals 5 of an inventive rotary seal arrangement. The rotary seals5 of each rotary seal arrangement are each disposed in a sealaccommodation structure constituted as a slot, of a stationary machinepart 3 and each seal a respective sealing surface of a rotating machinepart 2 constituted as the lateral surface of a cylinder. In each case, asupport element 20, a rubber-elastic contact body 21, and a sealing ring23 are provided. In each case, the contact body 21 is at least partiallydisposed in the axial direction of the rotatably mounted machine part 2between the support element 20 and the sealing ring 23. The contactbodies 21 are each disposed symmetrically around the sealing ring 23. InFIGS. 8 e and 8 h, two mutually separated contact bodies 21 areprovided. In FIG. 8 e, the support element 20 is constituted as acomponent facing away from the sealing edge and gripping round thesealing ring 23 and the contact body 21, e.g. made of sheet metal. InFIGS. 8 d and 8 g, the support element 20 is constituted by the slotedges of the seal-accommodating structure. For this purpose, noadditional separate support element is provided. In FIGS. 8 c and 8 d, aposition fixing element 90 disposed on both sides of the sealing ring isprovided in each case. Each of these position fixing elements 90prevents the contact body 21 and/or the sealing ring 23 from beingpressed too strongly onto the sealing surface 7.

A rotary seal arrangement is proposed with

-   -   a rotatably mounted machine part 2 and a machine part 3 that        forms a bearing for the rotatably mounted machine part 2,        wherein a first of the machine parts 3 constitutes a        seal-accommodating structure and the second of the machine parts        2 has a surface forming a sealing surface 7.    -   at least one rotary seal 5 disposed in the seal-accommodating        structure to seal a high-pressure area 10 against a low-pressure        area 11 between the machine parts 2,3.

The rotary seal 5 has an essentially rigid support element 20 that isdisposed essentially positionally stably with respect to the firstmachine part 3, a rubber-elastically deformable contact body 21 incontact with the support element 20 on the high-pressure area side, anda sealing ring 23 that has sealing edge 22 and sealing ring 23 that ispreferably loosely in contact with the contact body 21.

The sealing ring 23 has a wide side 24 on each side of the sealing edge22 and has a seal seat edge area 26 facing away from the sealing edgeand the wide sides 24 are interconnected via the seal seat edge area 26.The contact body 21 is at least partially disposed between at least oneof the wide sides 24 of the sealing ring 23 and the support element 20.

The invention is not limited to the embodiments stated above. Rather, anumber of variants are conceivable which make use of the characteristicsof the invention although fundamentally differently constituted.

1-10. (canceled)
 11. A rotary seal of a rotary seal arrangement, the arrangement having a rotatably mounted machine part and a machine part that forms a bearing for the rotatably mounted machine part, wherein a first machine part forms a seal-accommodating structure and a second machine part has a surface forming a sealing surface, at least one rotary seal being arranged in the seal-accommodating structure for sealing off a high-pressure, rotary feed-through area from a low-pressure area between the machine parts, wherein, through the rotary feed-through area, a fluid that is under positive pressure relative to the low-pressure area is introduced through a sealing surface, from one of the machine parts into the other of the machine parts, the rotary seal comprising: a support element, said support element being essentially rigid and positionally stable with respect to the first machine part; a rubber-elastically deformable contact body in contact with said support element on the high-pressure area side; and a sealing ring made from PTFE and having a sealing edge, said sealing ring having a wide side on each side of said sealing edge and a seal seat edge area facing away from said sealing edge, said wide sides being interconnected via said seal seat edge area, wherein said contact body is at least partially disposed between at least one of said wide sides of said sealing ring and said support element, said support element extending, at least in a supporting area, obliquely with respect to an axial direction of the rotatably mounted machine part, wherein said contact body is shaped in such a manner that, in the supporting area, the sealing ring is pressed away from the sealing surface by said contact body and, when exposed to pressure lying below a threshold pressure, said sealing edge seats in the rotary feed-through area without exerting a pressing load on the sealing surface or such that said sealing edge is separated from the sealing surface and, in the event of pressure exceeding the threshold pressure, the sealing ring and said sealing edge are pressed, in opposition to internal elastic forces of said contact body, towards the sealing surface to seat in a sealing manner thereon.
 12. The seal arrangement of claim 11, wherein said sealing ring is in loose contact with said contact body.
 13. The seal arrangement of claim 11, wherein the sealing surface is constituted as a lateral surface of a cylinder and said contact body is at least partially disposed, in an axial direction of the rotatably mounted machine part, between said support element and said sealing ring.
 14. The seal arrangement of claim 11, wherein the sealing surface is constituted as a circle area or a circular ring area and said contact body is at least partially disposed, in a radial direction of the rotatably mounted machine part, between said support element and said sealing ring.
 15. The seal of claim 11, wherein the second machine part is constituted as a radial shaft mounted in the first machine part and the rotary seal is ring-shaped and disposed about the radial shaft.
 16. The seal arrangement of claim 11, wherein said support element is constituted integrally with the first machine part as part of the seal-accommodating structure.
 17. The seal arrangement of claim 11, wherein said contact body extends, in a radial direction of the rotary seal, between said sealing ring and the seal-accommodating structure, said sealing ring being pretensioned in the radial direction toward the second machine part by an elastic restoring force of said contact body.
 18. The seal arrangement of claim 11, wherein said contact body has an area in contact with said sealing ring in an axial direction of the rotatably mounted machine part, on the high-pressure area side, wherein said edge of said sealing ring facing radially away from the sealing surface is disposed in a recess of said contact body.
 19. The seal arrangement of claim 11, wherein said sealing ring has a cross-section that is angled concavely with respect to the rotary feed-through area.
 20. The seal arrangement of claim 11, wherein said support element is made of steel and/or said sealing ring is made of PTFE and/or said contact body is made from an elastomer.
 21. The seal arrangement of claim 11, wherein two rotary seals are preferably disposed mirror-symmetrically about the high-pressure area. 